CN101298951A - Slice penetrating type mini channel heat exchanger with automatic solution dividing structure - Google Patents
Slice penetrating type mini channel heat exchanger with automatic solution dividing structure Download PDFInfo
- Publication number
- CN101298951A CN101298951A CNA2008101152720A CN200810115272A CN101298951A CN 101298951 A CN101298951 A CN 101298951A CN A2008101152720 A CNA2008101152720 A CN A2008101152720A CN 200810115272 A CN200810115272 A CN 200810115272A CN 101298951 A CN101298951 A CN 101298951A
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- heat exchanger
- pipe
- tube
- heat exchange
- lower collector
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- 230000000149 penetrating effect Effects 0.000 title claims description 11
- 239000007788 liquid Substances 0.000 abstract description 13
- 230000000694 effects Effects 0.000 abstract description 8
- 239000003507 refrigerant Substances 0.000 abstract description 5
- 238000001816 cooling Methods 0.000 abstract description 3
- 238000000926 separation method Methods 0.000 abstract description 3
- 238000003466 welding Methods 0.000 abstract 1
- 239000007789 gas Substances 0.000 description 11
- 239000012071 phase Substances 0.000 description 9
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 4
- 229910052802 copper Inorganic materials 0.000 description 4
- 239000010949 copper Substances 0.000 description 4
- 239000000203 mixture Substances 0.000 description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 4
- 230000005494 condensation Effects 0.000 description 3
- 238000009833 condensation Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 239000007791 liquid phase Substances 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 238000006056 electrooxidation reaction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 238000010257 thawing Methods 0.000 description 2
- 208000033999 Device damage Diseases 0.000 description 1
- 241000270295 Serpentes Species 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
- 230000009897 systematic effect Effects 0.000 description 1
- 238000009827 uniform distribution Methods 0.000 description 1
- 238000005406 washing Methods 0.000 description 1
- 239000002918 waste heat Substances 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
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Abstract
A thread type micro-channel heat exchanger with the own liquid separating structure includes an upper header, a lower header, a micro-channel zonal tube therebetween and fins passed through on the micro-channel zonal tube, wherein the fins and the airflow direction are arranged in certain slant angle, which improves the draining characteristics of the heat exchanger. According to the different depth of the zonal tube inserting into the lower header, the invention is divided into a heat exchanging tube playing the role of heat exchange and a communicating pipe playing the role of communication. The depth of the heat exchange tube for inserting into the lower header is larger, while the depth of the communicating pipe for inserting is smaller, thereby functioning as the automatic liquid separation when being used as the evaporator. The invention adopts the micro-channel zonal tube, which not only enhances the heat exchange in the tube but also advances the pressure resistance. The heat exchanger can adopt the integral welding technics with low contact thermal resistance. The heat exchanger has good heat exchange effect, small flow resistance, small charging quantity of the refrigerant, which is used in the household air condition, the commercial air condition or other places using the wind cooling heat exchange.
Description
Technical field
The utility model relates to a kind of slice penetrating type mini channel heat exchanger with automatic solution dividing structure, is used for the occasion of domestic air conditioner, commercial air conditioner or other and gas converting heat, belongs to air conditioner technical field.
Background technology
In refrigerated air-conditioning system, the most fin-tube heat exchanger that adopts of air-conditioner is made of coiled pipe and the fin that is through on the coiled pipe at present.Coiled pipe is that round copper pipe and multiplexer channel are parallel, and the heat exchanger of this structure is doing to need other knockout separatory when evaporimeter uses, otherwise will have the uneven problem of assignment of traffic in each pipe.The cold-producing medium that enters evaporimeter is a gas-fluid two-phase mixture, is divided into multichannel and enters and absorb heat in the evaporimeter, and liquid is evaporated to gas to realize the purpose of refrigeration air-conditioner.Can cold-producing medium two-phase fluid particularly wherein liquid be evenly distributed to and carry out the key that heat exchange is evaporator designs and structure in each paths.Because the variation of operating mode or knockout design are unreasonable when causing each road separatory uneven, will cause causing the tube refrigerant assignment of traffic inhomogeneous in actual motion, flow is less in the pipeline that has, and evaporate to dryness the excessive degree of superheat occurs in the pipeline outlet too early; And flow is too much in the pipeline that has, and outlet causes the too small degree of superheat, even contains partially liq.The two all makes the evaporimeter heat exchange area can not get sufficient utilization, has a strong impact on thereby systematic function caused.
When the cold-producing medium in entering each passage of evaporimeter was gas-liquid mixture, the volume of gas part was big, occupied bigger evaporimeter heat transfer space and area, caused that the evaporimeter heat exchange efficiency descends, bulky, cost improves.
Fin-tube heat exchanger adopts snake pipe, and the centre exists a plurality of elbows to change flow direction, and length is longer, and flow resistance is bigger, thereby makes condensation or evaporation process pressure drop bigger.The caliber of coiled pipe is bigger, and heat convection little than in the micro-channel tubes, and will reach certain heat exchange effect must charge into enough cold-producing mediums, and the cold-producing medium that charges into is unfavorable to environment finally by leaking or reason such as device damage is discharged in the atmosphere.
In addition, existing heat exchanger adopts copper pipe to wear the structure of aluminous fin outward usually, this structure relates to the contact of different materials, cause electrochemical corrosion easily, humid area or under wet cooling condition particularly, separate with copper pipe because of corrosion causes fin easily, increase the thermal contact resistance between copper pipe and fin greatly, the heat exchange effect obviously reduces.
The utility model content
At the prior art deficiency, the purpose of this utility model provides a kind of slice penetrating type mini channel heat exchanger with automatic solution dividing structure, to solve the problem that the evaporimeter inner refrigerant is not fully utilized and enters the refrigerant gas waste heat exchange area of evaporimeter at the inhomogeneous heat exchange area that causes of each channel capacity, improve the heat exchange effect, make it have the advantages that cost is low, simple in structure, heat exchange efficiency is high.Simultaneously, when heat exchanger during, be convenient to realize the switchover operation of condenser/evaporator as the off-premises station heat exchanger of heat pump type air conditioner.
The purpose of this utility model is achieved by the following technical solution:
A kind of slice penetrating type mini channel heat exchanger with automatic solution dividing structure, it is characterized in that: this heat exchanger comprises upper header 1, lower collector pipe 2, be arranged in the banded pipe in microchannel between the upper and lower collector, be through fin 5 and working medium entrance and exit on the banded pipe in microchannel, the banded pipe in described microchannel is made of communicating pipe 3 and heat exchanger tube 4, and described heat exchanger tube 4 inserts the lower collector pipe degree of depth greater than the lower collector pipe inside radius, and the degree of depth that described communicating pipe 3 is inserted lower collector pipe is equal to or less than the lower collector pipe inside radius; Described fin 5 becomes-40～40 ° to be in tilted layout with airflow direction; Described communicating pipe 3 is arranged one at least.
The subchannel hydraulic diameter of the banded pipe in microchannel is between 0.3～3mm in the utility model;
The working medium entrance and exit of heat exchanger described in the utility model can be arranged in the homonymy or the both sides of heat exchanger.
The utility model compared with prior art, have the following advantages and outstanding effect: the 1. slice penetrating type mini channel heat exchanger of the band automatic solution dividing structure that provides of the utility model, solved the uniform distribution problem of gas-liquid mixture in evaporimeter of cold-producing medium effectively, particularly when evaporimeter uses, solved the problem that causes waste of evaporimeter heat exchange area and heat exchange efficiency to descend because of the separatory inequality.And it all is liquid that the related liquid separation structure of the utility model makes the cold-producing medium that enters the evaporimeter heat exchanger tube, efficiently solve gas and enter evaporimeter and occupy heat exchange area and make the huge problem of evaporimeter volume, be expected to reduce the cost of evaporimeter or under the situation of same heat exchange area, obviously improve heat transfer property.2. the banded pipe in fin and microchannel is same material, connects to adopt and wears blade technolgy, has not only avoided because the electrochemical corrosion problem that materials chemistry character difference causes service life of equipment is obviously prolonged, and technology is simple, and is with low cost; 3. adopt the banded pipe in microchannel, its subchannel hydraulic diameter is at 0.3～3mm, and under identical flowing velocity, convection transfer rate is apparently higher than present used stock size pipe.4. used fin is in tilted layout along wind direction, and this arrangement helps managing the outer condensed water or the drainage of defrosting water, reduces the heat exchange thermal resistance of fin surface under wet cooling condition, helps strengthening and conducts heat, and improves the refrigeration machine efficiency.
Description of drawings
Fig. 1 is the slice penetrating type mini channel heat exchanger structural representation of band automatic solution dividing structure.
Fig. 2 is the fin structure schematic diagram.
Fig. 3 is a fin tilt layout schematic diagram.
Fig. 4 is the banded tube section schematic diagram of microchannel porous.
The specific embodiment
Below in conjunction with accompanying drawing structure of the present utility model and operation principle are described further.
Fig. 1 is the slice penetrating type mini channel heat exchanger structural representation of band automatic solution dividing structure, this heat exchanger comprises upper header 1, lower collector pipe 2, be arranged in the banded pipe in microchannel between the upper and lower collector, be through fin 5 and working medium entrance and exit on the banded pipe in microchannel, the degree of depth difference of thermal-collecting tube is divided into communicating pipe 3 and heat exchanger tube 4 to the banded pipe in described microchannel according to inserting down, heat exchanger tube 4 inserts the lower collector pipe degree of depth greater than the lower collector pipe inside radius, and the degree of depth that communicating pipe 3 is inserted lower collector pipe is equal to or less than the lower collector pipe inside radius; Described fin 5 becomes-40～40 ° to be in tilted layout with airflow direction; The degree of depth that is inserted in the lower collector pipe owing to communicating pipe 3 and heat exchanger tube 4 is different, thereby can realize gas-liquid separation automatically.Wherein the number of communicating pipe can be arranged one at least according to the needs of actual condition on the correspondence position of heat exchanger tube 4.The subchannel hydraulic diameter of the banded pipe in microchannel is at 0.3～3mm.The working medium entrance and exit of heat exchanger can be arranged in the homonymy of heat exchanger, also can be arranged in the both sides of heat exchanger.
When this heat exchanger uses as the evaporimeter of refrigerated air-conditioning system, enter evaporimeter from the refrigerant air-liquid two-phase mixture of throttling arrangement from the inlet of lower collector pipe 2, the gas-liquid two-phase cold-producing medium is after entering lower collector pipe 2, because the effect of gravity, the less gas phase of density flows on lower collector pipe top, the liquid phase that density is bigger flows in the lower part of lower collector pipe, gas-liquid interface of middle existence.Because heat exchanger tube is different with the degree of depth that is deep into lower collector pipe communicating pipe, gas phase will directly be communicated with upper header 1 and lower collector pipe 2 by communicating pipe 3, and flow to upper header along communicating pipe 3, liquid phase then flows to upper header 1 by the heat exchanger tube 4 that is deep into the lower collector pipe bottom, has realized that gas phase and the automatic of liquid phase separate.The heat of extraneous air passes to the interior cold-producing medium of pipe by the banded pipe itself of fin 5 and microchannel, cold-producing medium heat absorption evaporation.In the cold-producing medium evaporation process, the temperature of banded pipe in microchannel and fin is lower, moisture in the extraneous air may heat exchanger outside as fin on dewfall or frosting, the fin that is in tilted layout utilizes the effect with gravity of washing away of air-flow, helps condensed water or defrosting water is in time drained.
When this heat exchanger uses as condenser, at first enter heat exchanger from the inlet of upper header 1 from the high temperature and high pressure gas of compressor.The cold-producing medium that enter this moment is single-phase overheated gas, can be assigned to relatively equably in the banded pipe in each microchannel, banded pipe flows to lower collector pipe 2 along the microchannel then, in this process, by the outer surface and the fin 5 and outside air heat exchange worn thereon of the banded pipe in microchannel itself, thus constantly condensation, and condensation becomes single-phase subcooled liquid during to lower collector pipe 2, outlet outflow heat exchanger from lower collector pipe enters throttling arrangement.When using as condenser, the automatic solution dividing structure that the banded pipe in the microchannel by different depth in the lower collector pipe 2 constitutes does not play the separatory effect, does not influence flowing of the interior monophasic fluid of lower collector pipe yet.
The utility model not only can be used for various air-conditioners, and perhaps other is in the occasion of gas converting heat.
Claims (3)
1. slice penetrating type mini channel heat exchanger with automatic solution dividing structure, it is characterized in that: this heat exchanger comprises upper header (1), lower collector pipe (2), be arranged in the banded pipe in microchannel between the upper and lower collector, be through fin (5) and working medium entrance and exit on the banded pipe in microchannel, the banded pipe in described microchannel is made of communicating pipe (3) and heat exchanger tube (4), heat exchanger tube (4) inserts the lower collector pipe degree of depth greater than the lower collector pipe inside radius, and the degree of depth that communicating pipe (3) is inserted lower collector pipe is equal to or less than the lower collector pipe inside radius; Described fin (5) becomes-40～40 ° to be in tilted layout with airflow direction; Described communicating pipe (3) is arranged one at least.
2. according to the slice penetrating type mini channel heat exchanger of the described band automatic solution dividing structure of claim 1, it is characterized in that: the subchannel hydraulic diameter of the banded pipe in microchannel is between 0.3～3mm.
3. according to the slice penetrating type mini channel heat exchanger of the described band automatic solution dividing structure of claim 1, it is characterized in that: the working medium entrance and exit of heat exchanger is arranged in the homonymy or the both sides of heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2008101152720A CN101298951A (en) | 2008-06-20 | 2008-06-20 | Slice penetrating type mini channel heat exchanger with automatic solution dividing structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNA2008101152720A CN101298951A (en) | 2008-06-20 | 2008-06-20 | Slice penetrating type mini channel heat exchanger with automatic solution dividing structure |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101298951A true CN101298951A (en) | 2008-11-05 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2008101152720A Pending CN101298951A (en) | 2008-06-20 | 2008-06-20 | Slice penetrating type mini channel heat exchanger with automatic solution dividing structure |
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Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102235735A (en) * | 2010-05-05 | 2011-11-09 | 约克（无锡）空调冷冻设备有限公司 | Heat exchanger for heat pump system |
| WO2012100490A1 (en) * | 2011-01-26 | 2012-08-02 | 西安交通大学 | Condenser |
| CN101738011B (en) * | 2009-12-15 | 2012-11-21 | 清华大学 | Microfine multi-channel heat pump type air-conditioner heat exchanger with automatic liquid distribution structure |
| CN106247605A (en) * | 2016-08-24 | 2016-12-21 | 珠海格力电器股份有限公司 | Heat exchanger and vertical air conditioner with same |
| CN106440463A (en) * | 2016-12-02 | 2017-02-22 | 王志林 | Refrigerant heat pump micro-channel heat sink heating system and method |
| CN108709178A (en) * | 2018-04-26 | 2018-10-26 | 山东省食品药品检验研究院 | A kind of steam generator of Diameter of connecting pipe radial variations |
| US10247481B2 (en) | 2013-01-28 | 2019-04-02 | Carrier Corporation | Multiple tube bank heat exchange unit with manifold assembly |
| US10337799B2 (en) | 2013-11-25 | 2019-07-02 | Carrier Corporation | Dual duty microchannel heat exchanger |
| CN112368536A (en) * | 2018-07-11 | 2021-02-12 | 三菱电机株式会社 | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
| CN112594769A (en) * | 2020-12-24 | 2021-04-02 | 三峡大学 | Multi-energy supply device and method based on aluminum micro-channel heat pipe technology |
-
2008
- 2008-06-20 CN CNA2008101152720A patent/CN101298951A/en active Pending
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101738011B (en) * | 2009-12-15 | 2012-11-21 | 清华大学 | Microfine multi-channel heat pump type air-conditioner heat exchanger with automatic liquid distribution structure |
| CN102235735A (en) * | 2010-05-05 | 2011-11-09 | 约克（无锡）空调冷冻设备有限公司 | Heat exchanger for heat pump system |
| CN102235735B (en) * | 2010-05-05 | 2013-12-04 | 约克（无锡）空调冷冻设备有限公司 | Heat exchanger for heat pump system |
| WO2012100490A1 (en) * | 2011-01-26 | 2012-08-02 | 西安交通大学 | Condenser |
| US10247481B2 (en) | 2013-01-28 | 2019-04-02 | Carrier Corporation | Multiple tube bank heat exchange unit with manifold assembly |
| US10337799B2 (en) | 2013-11-25 | 2019-07-02 | Carrier Corporation | Dual duty microchannel heat exchanger |
| CN106247605A (en) * | 2016-08-24 | 2016-12-21 | 珠海格力电器股份有限公司 | Heat exchanger and vertical air conditioner with same |
| CN106440463A (en) * | 2016-12-02 | 2017-02-22 | 王志林 | Refrigerant heat pump micro-channel heat sink heating system and method |
| CN108709178A (en) * | 2018-04-26 | 2018-10-26 | 山东省食品药品检验研究院 | A kind of steam generator of Diameter of connecting pipe radial variations |
| CN112368536A (en) * | 2018-07-11 | 2021-02-12 | 三菱电机株式会社 | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
| CN112368536B (en) * | 2018-07-11 | 2022-04-15 | 三菱电机株式会社 | Heat exchanger, heat exchanger unit, and refrigeration cycle device |
| CN112594769A (en) * | 2020-12-24 | 2021-04-02 | 三峡大学 | Multi-energy supply device and method based on aluminum micro-channel heat pipe technology |
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Open date: 20081105 |